EP4067665A1 - Variable kühlmittelpumpen - Google Patents

Variable kühlmittelpumpen Download PDF

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Publication number
EP4067665A1
EP4067665A1 EP21382270.3A EP21382270A EP4067665A1 EP 4067665 A1 EP4067665 A1 EP 4067665A1 EP 21382270 A EP21382270 A EP 21382270A EP 4067665 A1 EP4067665 A1 EP 4067665A1
Authority
EP
European Patent Office
Prior art keywords
coolant
shaft
pump
impeller
variable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21382270.3A
Other languages
English (en)
French (fr)
Inventor
Carlos PERIBÁÑEZ SUBIRÓN
Fernando Miguel Gracia
Joaquín Roche Royo
José Luis Pomar Miguel
David Sebastián Solano
Gonzalo BAZÁN PÉREZ
Lidia GÓMEZ SANZ
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Airtex Products SAU
Original Assignee
Airtex Products SAU
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Airtex Products SAU filed Critical Airtex Products SAU
Priority to EP21382270.3A priority Critical patent/EP4067665A1/de
Publication of EP4067665A1 publication Critical patent/EP4067665A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • Coolant pumps for combustion engine vehicles may have a mechanical sealing of a main drive shaft to prevent the fluid from leaking to a driving pulley or the like.
  • the mechanical sealing requires a proper refrigeration to avoid premature failing. Fluid near the mechanical sealing of the main drive shaft may be fully or partially trapped and isolated because flow on that area may be restricted. A restricted flow does not allow the proper refrigeration of the mechanical sealing so a premature failure can be expected.
  • Some coolant pumps developed for reducing global fuel consumption and/or exhaust emissions in combustion engine vehicles are based on adjusting or regulating elements that fully or partially cover the outlet area of an impeller. This way, suitable operating temperatures of the engine may be achieved in a shorter period of time, e.g. a cold start.
  • a variety of solutions have been proposed to activate that adjusting element, for instance those mentioned in the background of the application DE102008026218B4 .
  • the adjusting or regulating elements may be driven in several ways. For instance, those elements may be driven based on pressurizing coolant drawn from the cooling system of the engine.
  • the coolant may be pressurized by an auxiliary pump. If the amount of coolant obtained from the cooling system is below a threshold value, the regulating element cannot be operated properly.
  • auxiliary pump may hinder the renewal of the coolant to the seal.
  • variable coolant pump comprises: a housing comprising an impeller area and a driving area, wherein the housing has a locking plate to define the impeller area at least partially; a shaft to rotate around an axis of rotation of the housing, wherein the shaft is operatively connected to a driving element arranged in the driving area; a main impeller to drive coolant in the impeller area, the main impeller being assembled in the shaft; a shutter displaceable in axial direction along the shaft to cover, at least partially, an outflow region of the main impeller such that an amount of the coolant delivered by the pump is variable; a control pressure pump to increase hydraulic pressure to displace the shutter, wherein the control pressure pump is assembled in the shaft; a first fluid path to feed the control pressure pump with coolant from the impeller area; a collector to collect driven coolant in a region between the main impeller and the locking plate, wherein the collector is in fluid communication with the first fluid path.
  • the coolant may be driven by rotation of the main impeller.
  • the coolant may flow through the impeller area, for example through an intermediate region arranged between the main impeller and the locking plate, with respect to the length of the shaft.
  • the coolant flowing in that intermediate region may flow following an angular direction or path with respect to the length of the shaft.
  • the path of the driven coolant may be substantially parallel to the locking plate, or at least a component thereof.
  • the collector may capture and conduct or lead a portion of the driven coolant circulating in the impeller area. Thanks to the collector, the kinetic energy carried by the driven coolant in the intermediate region may be used to enhance the flow rate through the first fluid path. This way, a suitable coolant flow rate to feed the control pressure pump may be achieved more easily and simply than a fluid path without a collector.
  • an orifice in the locking plate may be provided such that the direction followed by the circulating fluid in the intermediate region is substantially perpendicular to a first fluid path.
  • it may be complex to absorb through an orifice in the locking plate the coolant circulating in the intermediate region as it is in motion.
  • a resistance may be generated to absorb coolant through the first fluid path.
  • the pressure control pump has to generate a sufficient level of suction to obtain desired or predefined flow working requirements to actuate the shutter, e.g. a predefined volume of coolant.
  • the control pressure pump does not have to be oversized to ensure the proper amount of pressurized coolant to drive the shutter. If the control pressure pump is not to be oversized, the size of the control pressure pump may be kept significantly reduced. A control pressure pump of reduced size may require less energy for activation. Therefore, a more efficient coolant pump may be achieved. Furthermore, a control pressure pump of reduced size may occupy less room. Therefore, a space-saving coolant pump may be achieved.
  • a separation of coolant streams may be obtained through the pump of the first aspect.
  • the collector may also act as a stagnation point.
  • the collector may slow down or even stop the collected coolant relative to the rest of the coolant. This way, the collected coolant may avoid escaping, i.e. the collector may be a closed cavity that may create a backwater in which the collected coolant has proper or suitable conditions to be sucked in such as speed.
  • the collector may guide the collected coolant.
  • the collector may have a shape that favors the entry and channeling of the coolant to the first fluid path.
  • a collector's intake may be configured, for example oriented or faced, so as to draw or capture the coolant moving through the intermediate region. A portion of the coolant flowing in the intermediate region may pass through the collector intake.
  • the collector intake may be configured as a gate to capture the driven coolant.
  • the collector may be arranged over the locking plate or on the locking plate, for example the collector may lead at least a part of the coolant in a substantially parallel direction to the locking plate.
  • the locking plate may be substantially perpendicular to the length of the shaft.
  • the first fluid path may be in fluid communication with the collector intake through a duct.
  • a duct may mean a channel, passage, or conduit.
  • the collector and the first fluid path may be arranged with respect to each other such that an angle may be defined in the path of the coolant passing from the collector to the first fluid path, viewed in a longitudinal section of the pump. In some examples, the angle may be substantially about 90 degrees. However, this angle may vary. In examples, the collector and the first fluid path may be arranged to form an L-shaped junction therebetween.
  • the coolant may flow through the collector in a direction substantially parallel to the locking plate and may subsequently flow through a portion of the first fluid path substantially parallel to the shaft of the pump.
  • the collector may be arranged in such a way that a coolant flowing inside the collector may run substantially aligned with the driven coolant in the intermediate region, when seen in longitudinal cross section.
  • variable coolant pump may comprise: a shaft seal to prevent the coolant of the impeller area from reaching the driving area of the housing, wherein the shaft seal may be disposed in a seal chamber of the housing; wherein the seal chamber may be in fluid communication with the first fluid path, such that the coolant for feeding the secondary impeller passes at least partially through the seal chamber.
  • the shaft seal may receive a coolant flow.
  • a coolant flow may cool or keep the shaft seal's temperature within a suitable value range, i.e. a proper refrigeration of the shaft seal may be obtained. Therefore, a premature failure of the coolant pump may be avoided.
  • the seal's life may be extended.
  • the seal may be cooled by the collected coolant before reaching the control pressure pump. Coolant exiting from the control pressure pump, i.e. through the second fluid path, may be at a higher pressure than the coolant in the first fluid path. If the seal was cooled with coolant from the outlet of the control pressure pump, the seal could be subjected to more pressure than it may withstand and could fail or collapse. Owing to the present example, the seal is not cooled by coolant from the outlet of the control pressure pump.
  • control pressure pump may have a pump element slidably connected in axial direction to the shaft, the housing may comprise a cavity to receive the pump element, wherein the cavity may be configured to allow a relative displacement between the pump element and the shaft in axial direction.
  • the pump element may be connected to the shaft and may be displaceable along axial direction, i.e. length of the shaft. As no axial attachment between the pump element and the shaft may be defined, a mechanical transmission of the shaft rotation to the pump element may be done in a way that torque may be transmitted substantially without axial stress.
  • variable coolant pump may comprise: a second fluid path to discharge coolant from the control pressure pump into the impeller area; wherein the second fluid path may comprise a discharge bore arranged in the locking plate in such a way that a discharged coolant flows parallel to the shaft, at least partially.
  • the coolant circulating in the intermediate region may help to expel the coolant from the second fluid path, due to the Venturi effect. Thanks to this, the coolant may avoid getting stuck in the second fluid path. If the pressurized coolant remains in the second flow path, this could lead to accidental activation of the plug.
  • first and second fluid path has been respectively depicted with arrows in the accompanying drawings for the sake of clarity. These arrows may schematically indicate the path that the coolant may travel before and after passing through a pressure control pump.
  • variable coolant pump 1 In the following some examples of a variable coolant pump 1 will be described.
  • variable coolant pump 1 could be related to any kind of engine or the like.
  • the variable coolant pump 1 may be used for conveying and circulating a coolant or coolants.
  • Figure 1 schematically illustrates a partial longitudinal cross section view of a variable coolant pump 1 with a collector 12 according to an example when a regulation function is deactivated.
  • variable coolant pump 1 of Figure 1 comprises:
  • the coolant driven by the main impeller 4 may describe a generally annular path in the intermediate region IR in the direction of the length of the shaft 2.
  • the direction that the driven coolant may follow around the axis of rotation AR has been depicted as the arrow DC.
  • the collector 12 protrudes, at least partially, from the locking plate 10 toward the main impeller 4. This way, a step may be formed between the collector 12 and the locking plate 10.
  • the collector 12 may have a collector intake 15 located in the step. By arranging the collector intake 15 on the step, the collection of driven coolant may be optimized.
  • An intake bore 13 may be arranged between the collector 12 and the first fluid path 17.
  • the intake bore 13 may be located in the locking plate 10.
  • the intake bore 13 may be funnel-shaped.
  • the intake bore 13 may act as the first fluid path's intake, so as to feed the first fluid path 17.
  • the first fluid path 17 may be in fluid communication with the collector intake 15 through a duct 105.
  • the duct 105 may adopt any suitable shape to lead the coolant driven by the main impeller 4.
  • the duct 105 is nozzle shaped or bell-shaped. In this way, the inlet of the moving coolant between the main impeller 4 and the locking plate 10 may be facilitated.
  • the duct 105 may be defined between the locking plate 10 and a collector cover 14.
  • the collector cover 14 may be generally flat and attached to the locking plate.
  • the collector cover 14 may protrude with respect to the locking plate 10 towards the main impeller 4.
  • the locking plate 10 and/or the collector cover 14 may have a recess to form the duct 105.
  • the collector cover 14 is the one with a recess defining the path of the first fluid path 17. The latter can be seen for instance in Figures 1 and 2 .
  • the collector cover 14 may have a notch to define the track of the duct 105.
  • the collector cover 14 may separate the coolant captured by the collector 12 from the remaining coolant driven by the main impeller 4.
  • the characteristics of the captured coolant such as speed and/or pressure may be suitably adjusted before entering the first fluid path 17.
  • the duct 105 may be arranged such that a section of its length is perpendicular to the shaft 2.
  • the path that the collected coolant follows through the interior of the collector may change direction when it enters the first fluid path 17 of the pump 1.
  • the duct 105 may be arranged such that a section of its length is substantially parallel to the locking plate 10.
  • the duct 105 may be arranged such that a portion of its length is rounded about the shaft 2 or tangential to the shaft 2. In this way, the coolant collected by the collector 12 may be smoothly conveyed to the first fluid path 17.
  • the intake bore 13 may be generally rounded and/or elongate to follow, at least partially, the rounded portion of the duct 105.
  • the collector intake 15 may be directly connected to the first fluid path 17.
  • the pump 1 does not comprise a duct.
  • the collector 12 may be arranged, at least partially, on the locking plate 10.
  • the duct 105 may present a generally curved layout when viewed in plan, as seen in figure 2 .
  • This curved layout may be adapted to the circular path that the coolant may follow in the intermediate region.
  • This curved shape may facilitate the collection of driven coolant.
  • the collector intake 15 may comprise at least one rounded wall.
  • This rounded wall may be a side wall of the curved layout.
  • the rounded wall may provide a significantly smooth entry of the collected coolant.
  • variable coolant pump 1 may comprise:
  • the first fluid path 17 followed by the coolant from the impeller area 101 to the inlet 18 may comprise the seal chamber 16 where the shaft seal 5 is placed. Therefore, the coolant suctioned by the secondary pump 8 may keep the shaft seal 5 at a proper temperature to avoid a premature failure.
  • control pressure pump 8 may have a pump element 81 slidably connected in axial direction to the shaft 2, the housing 100 may comprise a cavity 103 to receive the pump element 81.
  • the cavity 103 may be configured to allow a relative displacement between the pump element 81 and the shaft 2 in axial direction as depicted by arrows 82. This may facilitate installation tasks or smooth operation of the pump as clearances between parts may be compensated or absorbed by axial displacement of pump element 81 relative to shaft 2.
  • the pump element 81 may be made of a material with flexible features.
  • control pressure pump 8 may comprise a secondary impeller as the pump element 81 which may be arranged coaxially with the shaft 2, the secondary impeller may be driven by the shaft 2.
  • variable coolant pump 1 may comprise:
  • the locking plate 10 may be arranged between the impeller area 101 and the cavity 103.
  • the locking plate 10 is provided between the impeller area 101 and the control pressure pump 8.
  • the locking plate 10 extends beyond the cavity 103 in plan view but the locking plate 10 may be limited to the extension of the cavity 103 in plan view.
  • the locking plate 10 may be attached in a fixed manner to the housing 100, for instance, by several fixation elements 11.
  • a lid 83 may define along with the cavity 103 a room to receive the control pressure pump 8 as can be seen in Figure 1 .
  • the lid 83 may be arranged between the cavity 103 and the locking plate 10 in axial direction.
  • the lid 83 may comprise an annular body.
  • a return spring 36 may be placed between the shutter 7 and the housing 100 as seen in Figure 4 .
  • the return spring 36 may push the shutter 7 back to its deactivated position. This may occur when the control valve 27 is deactivated after having been activated.
  • variable coolant pump 1 may further comprise a control valve 27 to control the flow rate or pressure of the coolant from the outlet 20 of the control pressure pump 8 to the impeller area 101.
  • the control valve 27 may control the flow rate and/or pressure of the second fluid path 19.
  • An example of control valve 27 can be seen in Figures 3 - 6 .
  • the control valve 27 may be any type of valve which may allow controlling the flow of coolant such as a solenoid valve.
  • pressurized refrigerant begins to accumulate driven by the control pressure pump 8, see Figure 4 .
  • a pressure is generated in the second fluid path 19 that may reach the pressure threshold.
  • the return spring 36 may be compressed, so that the plug 7 may gradually limit the outflow of refrigerant from the output region OR. See for instance, Figure 5 . If the control valve 27 is subsequently opened, the coolant may follow the second fluid path 19 until the discharge bore 110.
  • the discharge bore 110 may be positioned in the locking plate so that there is substantially no fluid interference between the collector intake and the discharge bore 110.
  • the collector intake and the discharge bore may be arranged diametrically opposite each other.
  • the following describes the operation of the pump 1 according to an example.
  • the pump shaft 1 may rotate thanks to the impulse received through the driving element 3, for example, from the crankshaft of the combustion engine.
  • the main impeller 4 may also rotate due to the rotation transmitted by the shaft 2.
  • the coolant present in the impeller area 101 may in turn be driven due to the rotation of the main impeller 4.
  • Part of that driven coolant flows in the intermediate region IR between the main impeller 4 and the locking plate 10. In that region, part of the driven coolant may follow a substantially annular path around the shaft 2 due to the impulse that may be applied by the main impeller 4.
  • the collector 12 may receive part of the coolant flowing through the intermediate region IR.
  • the coolant collected by the collector 12 may continue through the duct 105 in case the pump 1 has one.
  • the properties of the coolant such as pressure and/or speed may be modified with respect to those of the coolant flowing through the intermediate region IR. If the duct 105 has a rounded or curved portion around the shaft 2, the collected coolant may follow a path or way similar to that carried by the coolant that runs through the intermediate region IR.
  • the collected coolant may pass through the intake bore 13 and enter the first fluid path 17.
  • the collected coolant may retain at least a part of the kinetic energy obtained due to the rotation of the main impeller 4.
  • the collected coolant may continue along the first fluid path 17.
  • the coolant passes through the seal chamber 16 and from there goes to the inlet 18 of the pressure control pump 8. In the case of not passing through the seal chamber, the coolant would go to the inlet 18.
  • the coolant flows through the seal chamber 16 it may cool the shaft seal 5.
  • the path of the first fluid path 17 may be implemented thanks to the kinetic energy carried by the coolant as explained above and to the suction exerted by the control pressure pump 8.
  • Coolant may exit the control pressure pump through the outlet 20. Passage through the control pressure pump 8 may cause the pressure of the coolant to increase.
  • the coolant pressurized by the control pressure pump 8 may continue through the second flow path 19 as shown in Figure 4 . If the control valve 27 is open or inactive, the shutter 7 remains in its retracted position as shown in Figure 6 .
  • the coolant may continue through the second flow path 19 as shown in Figures 7 and 8 until it reaches the discharge bore 110.
  • control valve 27 If the control valve 27 is activated or closed, at least partially, it does not allow at least a portion of the coolant pressurized by the pressure control pump 8 to reach the discharge bore 110. A pressure may build up in the section of the second fluid path 19 from the outlet 20 to the control valve 27 as seen in Figure 4 . If a pressure threshold is reached, the resistance of the return spring 36 can be overcome and the plug 7 may be extended to at least partially shut off the outflow region OR as shown in Figure 5 . A motor control unit (not shown) may send a command to actuate the control valve 27. When the control valve 27 is opened, pressure inside the second fluid path 19 may be reduced because coolant may be allowed to flow through the control valve 27 as seen in Figure 6 .
  • the first fluid path 17 and the second fluid path 19 may have several sections or regions as set forth in the following:
  • the housing 100 may have a piston chamber 75 to receive at least one end portion of the shutter 7, the end portion being arranged at an opposite side to the main impeller 4, see Figure 5 .
  • the piston chamber 75 may be annular shaped around the axis of rotation AR.
  • the shutter 7 may have a pressure ring 71 around the axis of rotation AR, see Figure 5 .
  • the pressure ring 71 may be configured to move within the piston chamber 75 in a direction of the length of the shaft 2.
  • the pressuring ring 71 may move within the piston chamber 75 when the shutter moves to or from the main impeller 4.
  • the pressure ring 71 may be in fluid communication with the second section SS of the second fluid path 19 through a shutter feeding channel 74. This way, if the control valve 27 is at least partially closed, the pressure inside at least the second section SS may rise as above described and the built-in pressure coolant may apply a force and so a pressure to the pressure ring 71.
  • the applied pressure to the ring 71 above the pressure threshold may compress the spring 36.
  • the pressure ring 71 may have a cross section having an indentation 73 in the side of the coolant which may create a ring channel 72 about the axis of rotation AR.
  • the pressurized coolant may flow through the ring channel 72 around the axis of rotation AR. In this way the pressure within the ring channel 72 may be distributed substantially homogeneously. This may mean that the activation of the shutter 7 may be uniform around the axis of rotation AR, i.e., the outflow region OR may be shut off uniformly around the axis of rotation AR.
  • the shutter feeding channel 74 may be oriented towards the ring channel 72 to further improve the filling of the ring channel 72 and so a homogeneous distribution of the pressurized coolant between the piston chamber 75 and the pressure ring 71 may be achieved.
  • the indentation 73 may be generally U- or V-shaped.
  • the pressure ring 71 may have a planar surface in the side of the spring 36.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP21382270.3A 2021-03-31 2021-03-31 Variable kühlmittelpumpen Pending EP4067665A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21382270.3A EP4067665A1 (de) 2021-03-31 2021-03-31 Variable kühlmittelpumpen

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21382270.3A EP4067665A1 (de) 2021-03-31 2021-03-31 Variable kühlmittelpumpen

Publications (1)

Publication Number Publication Date
EP4067665A1 true EP4067665A1 (de) 2022-10-05

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EP21382270.3A Pending EP4067665A1 (de) 2021-03-31 2021-03-31 Variable kühlmittelpumpen

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011018240A1 (de) * 2011-04-19 2011-11-24 Tcg Unitech Systemtechnik Gmbh Radialpumpe mit einem in einem Gehäuse drehbar gelagerten Laufrad
DE102008026218B4 (de) 2008-05-30 2012-04-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
EP2698541A2 (de) * 2012-08-14 2014-02-19 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit verstellbarem Fördervolumen, insbesondere zum Verstellen einer Kühlmittelpumpe
DE102013111939B3 (de) * 2013-10-30 2014-10-30 Pierburg Gmbh Kühlmittelpumpe für den Einsatz im KFZ-Bereich
DE102013222828A1 (de) * 2013-11-11 2015-05-28 Schaeffler Technologies AG & Co. KG Abdichtung eines Pumpkolbens für eine Aktuatorik einer Kühlmittelpumpe
EP3290713A1 (de) * 2016-09-06 2018-03-07 Pierburg GmbH Kühlmittelpumpe für den kfz-bereich sowie ein kühlmittelkreislauf für eine verbrennungskraftmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008026218B4 (de) 2008-05-30 2012-04-19 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102011018240A1 (de) * 2011-04-19 2011-11-24 Tcg Unitech Systemtechnik Gmbh Radialpumpe mit einem in einem Gehäuse drehbar gelagerten Laufrad
EP2698541A2 (de) * 2012-08-14 2014-02-19 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit verstellbarem Fördervolumen, insbesondere zum Verstellen einer Kühlmittelpumpe
DE102013111939B3 (de) * 2013-10-30 2014-10-30 Pierburg Gmbh Kühlmittelpumpe für den Einsatz im KFZ-Bereich
DE102013222828A1 (de) * 2013-11-11 2015-05-28 Schaeffler Technologies AG & Co. KG Abdichtung eines Pumpkolbens für eine Aktuatorik einer Kühlmittelpumpe
EP3290713A1 (de) * 2016-09-06 2018-03-07 Pierburg GmbH Kühlmittelpumpe für den kfz-bereich sowie ein kühlmittelkreislauf für eine verbrennungskraftmaschine

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